Variable-speed power transmission



y 1945- G. M. HARRY VARIABLE SPEED POWER TRANSMISSION Filed Jan. 21, 1944 5 Sheets-Sheet l n n t MW BY a??? QM; I

Gwffrg M 22, 1945- G. M. HARRY 2,376,429

VARIABLE SPEED POWER TRANSMISSION Q: a INVENTOR.

Geaffr ujiffla 7 G. M. HARRY VARIABLE SPEED POWER TRANSMISSION May 22, 1945.

Filed Jan. 21, 1944 5 Sheets-Sheet 3- IN V EN TOR.

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May 22, 1945. e. M. HARRY VARIABLE SPEED POWER TRANSMISSION Filed Jan. 21. '1944 5 Sheets-Sheet 4 IN V EN TOR.

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May 22, 1945. G. M. HARRY VARIABLEYSPEEYD POWER TRANSMISSION Filed'Jan. 21, -1944 5 Sheets-Sheet 5 INVENTOR. [if

Geoff Patented May 22, 1945 2,316,429 VARIABLE-SPEED rowan TRANSMlSSION Geoffrey M. Harry, Oak Park, Ill.

Application January 21, 1944, Serial No. 519.6115

21 Claims.

This invention relates to a variable speed transmission and more particularly to an all-gear speed changing apparatus that is infinitely variable within a certain predetermined range of adiustment and by which the constant torque of a driving or input shaft may be transmitted to a driven or output shaft in infinitely varying degrees of speed.

Heretofore, there have been devised numerous types of variable speed transmission mechanisms for varying the speed of a driven member with respect to the constant speed of a driving. member. These mechanisms involved the use of stepped-cones, conical faced discs with connecting V-belts, numbers oi. gears operably connected in a train with a set amount of possible speeds, parallel andopposite conical faced pulleys with connecting belts, purely frictional mechanisms, and many other divers types of combinations. However, such well known types of variable speed mechanisms were limited in their'application or use. In some it was possible to vary the speed of the driven member only from certain predeterminedset speed ratios to others within a certain range of adjustment. These were not infinitely variable. For instance, within a given range of adjustment the speed of the driven member could be varied to but two, three, four, five, six, etc., difierent speeds but to those set speeds only. Such mechanisms were of little utility in instances wherein a speed adjustment to a point betweenthe predetermined steps of speed was required by the nature of the machine or tool being operated or the work being done. Such mechanisms also had a further recognizeddisadvantage. In order to make the adjustment from one speed to another, it was necessary to stop and disconnect the variable speed mechanism from driving engagement with the driven machine,

tool, or work being done, thus causing the ma- 4 chine or tool to remain idle for the corresponding P riod. v

Likewise, the use of variable speed mechanisms such as the conical faced disc or pulley type with connecting belts wherein the principle of friction between contacting surfaces was employed for obtaining variations in the speed of the driven mem ber was also relatively limited. On account of the great slippage between the friction surfaces under load only very light loads could be transmitted, and hence they were of little utility in the power field; These mechanisms were not of were incapable of constant and uninterrupted us age due to shutdowns for friction surface renewals.

In addition, some attempts have been made to devise speed transmission mechanisms which were infinitely variable within a predetermined range. However, for varying reasons these attempts have proven relatively unsuccessful. Some were found to be relatively inefllcient in that a great amount of power was required and a considerable portion of that power was lost in transmission between the driving and driven members. Others were undesirable because they were large, cumbersome and expensive; and still others possessed such an arrangement between the moving parts that those parts were subject to undue-wear resulting in their relatively short life and requiring con stant replacement. This replacement of parts was not only expensive as far as the cost of the parts was concerned but the various machines or tools to which the power was being transmitted were forced to stand idle during the repair period,

the positive power transmission 't"'pe. Further,

such mechanisms were subject to great wear between the friction surfaces, and as a result they thereby increasing production costs. The above referred to and other inherent disadvantages in all the various types of speed reducers have been well known to skilled workers in the field for years. These disadvantages have necessarily been tolerated for want of a satisfactory solution.

It is, therefore, an object of my invention to provide an improved power transmission mechanism which is variable in speed to all infinite degrees or variations within a predetermined range of adjustment.

Another object of my invention is to provide an infinitely variable power transmission mech-: anism which is of the all-gear type whereby a positive transmission of power can be maintained at every instant of operation and in which the wear of the moving parts has been reduced to a minimum.

Still another object of my invention is to provide an improved power transmission mechanism by which the speed of the driven member may be infinitely varied within a certain range of ad iustment with respect to the speed of the driving member during the operation of the mechanism in the transmitting of power without disengaging the mechanism from operative engagement with the driving member or the source of power.

A further object of the invention is to provide a. power transmission mechanism having such an arrangement and combination of parts that when the load of the work is applied to the driven or output shaft, a reaction results backwardly through the mechanism which tends to drive the mechanism itself and the driving shaft or member in the same direction as it is already being driven by the source of power, thereby reducing the loss of power between the driving and driven member to a minimum.

Still further objects of the invention are to provide a power transmission mechanism that is of compact and simple construction, relatively inexpensive to manufacture, and is a self-contained unit which has a wide range of adaptability to all types of mechanisms, meachinery and tools now in operative use.

Other and further objects and advantages of the present invention will become apparent as this description progresses, reference being had to the accompanying drawings, wherein:

Figure 1 is a horizontal sectional view of the improved power transmission mechanism comprising my invention;

Fig. 2 i a vertical sectional view of the power transmission mechanism taken on the line 2-2 in Fig. 1 looking in the direction of the arrows;

Fig. 3 is a detailed vertical sectional view of the mechanism for adjusting the movable gear to its various eccentric position and showing the relative positions of the parts of such mechanism with the gear adjusted to eccentric position;

Fig. 4 is a vertical sectional view of the power transmission mechanism taken on the line 44 of Fig. 1 looking in the direction of the arrows;

Fig. 5 is a vertical sectional view of the mechanism taken on the line 5-5 of Fig. 1 looking in the direction of the arrows;

Fig. 6 is a side view of the mechanism illustrated in' Fig. 5 as viewed from the right; and

Fig. 7 is avertical sectional view similar to that of Fig. 4 but illustrating the eccentrically extending curved end wall I3, and vertical side each of the side walls thereof. An output shaft or driven sleeve 26 which also extends through the side wall M of the casing I0 is mounted on the left end of the shaft and is separated therefrom for free and independent rotative movement by bushings 26a and 26b. The input shaft 25 is adapted to be operably engaged for rotative movement at a constant speed with a suitable source of power (not shown) and the output shaft or driven sleeve 26 is. adapted to be operably engaged with a machine, tool or the like, which must be operated at a speed at variance with that of the source of power. The variable speed or power transmission mechanism, which will be described in detail hereinafter, operably connects through its train of gears andshafts the input and output shafts 25 and 26 and this transmission mechanism may be adjusted during its operation merely by the turning of a crank handle 21, which is mounted on the outside of the casing I 0, so as to vary the speed of the driven sleeve 26 to any infinite degree within a certain range of adjustment.

walls I4 and i5. A cover plate I6 which comwithin the casing I!) may be operated in an oil bath and consequently the cover plate I0 is provided with a centrally located threaded opening 2| through which oil may be pouredinto the casing l0, and likewise the side wall I4 is provided at the bottom thereof with a threaded opening 22 through which used oil may be drained from the casing. The casing openings 2| and 22 are sealed by screw plugs 23 and 24.

Referring to Figs. 1 and 2 of the drawings, a driving member orinput shaft 25 [extends trans-. versely of the casing l0 and projects through As shown in Fig. 1, the driving shaft 25 is mounted for rotative movement at its right end in an annular ball bearing member 28 which is set in and supported by the casing wall l5. Adjacent the bearing member 28, an annular oil seal 29 encircles the shaft 25 and serves to prevent the passage of oil from the interior of the casing Ill. The opening 30 in the casing ll) through which the right end of the driving shaft 25 are tends is closed by a plate member 3i which is bolted to the casing and which also serves to retain the oil seal 29 in proper sealing position. The closure plate 3| has a centrally located aperture 3la through which the end of the shaft 25 supported by the driven sleeve 26 which in turn is supported for free rotative movement by roller bearings 32 which are set in and supported by the end wall I4 of the casing l0. An annular oil seal 33 encircles the driven sleeve 26 adjacent the roller bearings 32 and, similarly to oil seal 29,-also prevents the passage of oil from-the casing I0. The opening 34 in the casing I 0 is closed by a plate member 35 which likewise is bolted to the casing I 0 and is provided with a centrally located aperture 35a through which the end of the driven sleeve26 projects for operable connection to the machine or tool to be operated.

Within the casing l0 and operably connecting the driving shaft 25 to the driven sleeve 26 is a planetary gear train comprising a sun gear 31 which is keyed tothe driving shaft 25 and constantly in mesh with two diametrically opposed planet gears 38. These planet gears 38 are mounted on short shafts 40 carried by an annular disc member 4! which is integrally formed with the driven sleeve 26 at its inner end andat substantially right angles thereto. The planet gears 38 are also constantly in mesh with an internal or orbit gear 42 which is integrally formed on the left end (as viewed in Fig. 1) of a sleeve member 43. This sleeve member 43 is mounted for free and independent rotative movement on bushings 43a. and 4317 which are carried on the central portion of the driving shaft 25 within the casing Ill. The sleeve member 43 is provided with radial openings 430 to facilitate the passage of oil to the shaft, 25 for proper lubrication of the moving parts.

As viewed in Fig. 4, when the shaft 25 is driven 2,376,429 in a counterclockwise direction by the source of' power, the sun gear 31 likewise is rotated in a counterclockwise direction which causes the planet gears 38 and the internal gear 42 to rotate in a clockwise direction. However, as the planet gears 38 rotate clockwise they are caused to move in a'fiquzterclockwise direction in their orbit The varying and controlling of the speed of the driven sleeve 26 is accomplished by'varying and controlling the speed of the internal gear 42 of the planetary train. For example, if the internal gear 42 were to be constrained against any rotative. movement whatsoever, the driving shaft 25 would effect rotative movement of the driven sleeve 26 at its highest rate of speed, since the planet gears 38, upon being rotated by the sun gear 31, would have a stationary gear member 42 to work back against so as to move, therefore, at their highest rate of speed in a counterclockwise direction (as viewed in Fig. 4) about the sun gear 81 and within the internal gear 42. In

. other words, with the internal gear stationary,

none of the speed of movement of the planet gears 38 around the internal gear 42 would be lost, as is the case when rotative movement of the internal gear 42 in the same direction of rotative movement of the planet gears 38 is permitted. Consequently, if the internal gear 42 is caused to rotate in a clockwise direction at a relatively slow rate of speed, the driven sleeve 26 will be caused to rotate in a clockwise direction at a relatively high rate of speed. And, thus, as the rate of rotation of the internal gear 42 in a clockwise direction is increased, the rate of speed of rotation of the driven sleeve 26 will be decreased proportionately as a consequence. Conversely, as the rate of rotation of the internal gear 42 is decreased, the rate of rotation of the driven sleeve 26 will be increased. Should the speed of rotation of the internal gear 42 be increased to very high degrees, the planet gears 38 may be caused to remain stationary in their orbit or even to move in a clockwise direction and thereby causing rotative movement of the driven shaft 26 in a clockwise or reverse direction. The rate of rota-. tion of the internal gear 42 is controlled by the following mechanism which will now be described.

As shown more particularly in Figs. 1 and 2 of the drawings, a pinion 44 is keyed to the driving shaft 25 between the right end of the sleeve 43 and the casing side wall i5 and meshes with a large gear 45 keyed to a rotatable shaft 46. The shaft 46 extends transversely of the casing ID in parallel relationship to the driving shaft 25 and in substantially the same plane therewith as shown in Fig. 2. Each end of the shaft 46 ismounted for rotative movementin roller bearings 41 and v end wall flange l8. Annular closure plates 53 and 54 which serve to maintain the roller bearings 41 and 48in proper operative position and also to close the annular casing openings are bolted to the casing I0 by bolts 53a and 54a. The roller bearings 41 and 48 are provided with-grease nipthe closure plates 53 and 54.

Mounted on the rotatable shaft-46 substantially centrally of its ends is a gear 68 (Figs. 1, 2 and 4) which is adapted to be moved radially 'or outwardly from concentric position, as shown in Fig.

4, with respect to the shaft 46 to eccentric position and return so as to effect (in a manner to be fully described hereinafter) an increase or a decrease in the rate of rotation of the internal gear 42. This eccentrically movable gear 681 is slidably mounted on a rotatable supporting member 6| having a portion 6| 0. of rectangular crosssection which is received within an elongated rectangular opening 62 extending through'the body portion of the gear 66 for sliding engagement therewith. The supporting member 6| is keyed to the shaft 46 so that the gear 681s caused to rotate upon rotation of the shaft 46.

The eccentrically slidable gear 68 in its concentric position, shown clearly" in Fig. 4, is in mesh with eight smaller gears 64 which in turn mesh with eight still smaller gears 65. Each of the gears 64 and 65 is carried by and between rockable bracket members 61 and 68, the gears 64 being made integral with short shafts 69 extending between the rockable brackets 61, and 68 and the gears 65 being made integral with relatively longer rotatable shafts 18 which extend between and through the brackets 61 and] 68 The shafts 16 are supported outside of the rockable brackets 61 and 68 by a pair of standard plates 12 and 13 which are bolted to the bottom wall ll of the casiing I0 and extend vertically ln'parallel relation with each other to a point spaced somewhat below the cover plate 16 The shafts 69 and 10 are adapted to run freely in bushings 69a and 160,- respectively, in the brackets 61 and 68, and the shafts 10 also run freely in bushings: 12a and 13a in the standard plates 12 and 13 The outer ends of each of the eight pairs of rockable brackets 61 and 68 are maintained in properly'spaced relationship by spacing members 14, the brackets 61, 68 and their respective spacing members 14 being secured together by bolts 15 extending therethrough.

Keyed on the right ends (as viewed in Figs 1 and 2) of each of the eight rotatable shafts 10 are pinions 16, each of which is in constant mesh at all times with a common gear 11 which is secured to the inner face of a relatively larger gear 18 by means of bolts 19. The gear 11 may be integral with gear 18, if desired. The gear 18 is integrally formed as a part of a sleeve or'hub which is mounted on a bushing 80a on the rotatable shaft 46 for free rotatable movement independently of said shaft The hub 88 is provided with diagonal openings 8% leading to openings 860 in the bushing 88a to facilitate the passage of oil to the shaft 46 for proper lubrication 45, the eccentrically movable gear 68, the gears 64, the gears 65, the pinions 16, the gear 11, the

' gear 18, the gear 8|, the sleeve 43 and finally to ples'51 and 58, respectively, which extend through mal concentric position illustrated in Fig. 4 of the drawings, the internal gear 42 is driven at its slowest rate of speed with the result that the driven sleeve 26 is caused to rotate at its highest rate of speed.

If, however, it is desired to reduce the rate of speed of the driven sleeve 26, the rate of speed of the internal'gear 42, as explained hereinbefore, is correspondingly increased by outward movement of the gear 60 to eccentric position with respect to the shaft 46. Outward movement of the gear 60 to eccentric position is accomplished by turning the crank handle 21. The operating handle 21 is secured by means of a set screw 90 to the outer end of an adjusting screw III which extends within the casing I through the upper side of the cover plate I6. Threadedly engaged with the adjusting screw 9| adjacent its inner end, is a nut 93 having laterally extending pins 94 on each side thereof which are received within elongated vertical slots 95 in the upwardly directed arms 96 and 91 of a bifurcated lever member 98. The lever 98 is secured to a rock shaft 99 by a set screw I00, the rock shaft 99 being supported for free rotative movement at its left end, as viewed in Fig. 5, by hearing members I 0I and I02 and at its other end by a bearing member I03, which bearing members IOI, I02 and I 03 are bolted to the outer side of the upright standard plate 12.

The lowerend of the lever 98 is provided with a semi-circular bifurcated end portion I04 which I straddles a slidable collar I05. Each of the ends of the semi-circular portion I04 of the lever 98 is provided with elongated slots I06 and I01, respectively. The slidable collar I05 is comprised of a central body portion I08, which is s'lidably keyed to the shaft 46 for rotative movement therewith and provided at its ends with integral upstanding annular flanges I09 and H0 also encircling the shaft 46. The body portion I08 and end flanges I09 and H0 form a structure resembl-ing a spool adapted for rotative movement with; the shaft 46 and also for slidable axial movement thereon. Encircling the central body portion I08 of the collar I 0 5 and confined between its end flanges, I09 and H0 is a split ring member II I which is independent of and unaffected by rotative movement of the body portion I00 which is free to rotate within the ring member I III. The split ring member III is provided with laterally projecting pins I I2 and I I3 which are received within the elongated slots I06 and I01, respectively, of the ends of the lever 98.

The upstanding end flange IIO of the slidable collar I05 is provided with a forwardly directed arm I I I to which is pivotally connected the downwardly extending arm of a bell crank lever II5. This lever H5 is pivotally supported on a pivot pin H6 extending between two projecting ears 6) of the gear supporting member 6|, and has a forwardly directed arm I I1 having an enlarged ball-like end I I8 whichis received within a square opening or socket 9 extending through the gear 60. The square opening H9 and the rectangular slide opening 62 are in alignment and are located on substantially the same diameter of the gear 60.

Movement of the gear 60 to an eccentric position is accomplished by operation of the foregoing mechanism. To this end, the operator may rotate the crank handle 22 so as to cause the nut to rock the lever 98 in a counterclockwise direction, as viewed in Fig. 2. This counterclockwise movement causes the lower semi-circular portion I04 of the lever 98 to move forwardly and slide the collar I05 axially toward the gear 60 along the shaft 46 which in turn rocksthe bell crank lever I I5 in a counterclockwise direction about its pivot II 6. This movement causes the ball-like end II8 to be raised or move away from the. shaft 46, thereby forcing the movable gear 60 to slide upwardly on its supporting slide block He in a direction outwardly from the shaft 46 to an eccentric position clearly shown in Fig. 7 of the drawings.

In order to compensate for the transposition of the mass of the gear 60 to eccentric position and thus provide for a balanced drive, there is provided a counterbalance I32 which is pivotally supported by pairs of arms I33 and I34 pivotally connected to the end portion IIO of the sliding collar I05 and the lower end of the projecting ears 6| b of the gear supporting member 6|, respectively. With the foregoing arrangement, as the sliding collar I 05 moves to the right, as viewed in Fig. 2, so as to effect movement of the gear 60' to outward eccentric position away from the shaft 46, the counterbalance I32 also is moved in the opposite direction away from the shaft 46 a proportionate distance.

Simultaneously with the movement of the gear 60 to an eccentric position, the eight smaller gears 64, all of which are in meshing engagement with the gear 60 when that gear is in concentric position, are also caused to be moved outwardly in substantially radial directions away from the shaft 46. Since all the gears 64 move outwardly in all directions away from the shaft 46, some of these gears 64 will pull away from-meshing engagement with the eccentric gear 60, the number of gears 64 in meshing engagement with the gear becoming more reduced in number as the gear 60 continues to move toward its extreme eccentrio position. However, while moving to and While in eccentric position, the gear 60 is in mesh with one or more of the gears 64 at all times, as will be more fully explained hereinafter.

Movement of the gears 64 to their outward positions also occurs as the crank handle 21 is rotated by the operator. When the lever 98 is rocked counterclockwise as viewed in Fig. 2, the rock shaft 99 also rocks in a counterclockwise direction, causing a link I20,- which is pivotally connected at its upper end to a lever I 2 I, to move upwardly, as viewed in Figs. 1 and 5. In detail, the lever I2I has a laterally extending arm I22 which extends between the upwardly directed bifurcated ends I23 and I24 of the link I20, these bifurcated ends I23 and I24 and the arm I22 being pivotally connected by means of a pivot pin I25 extending through said elements. The lower end of the link I20 is pivotally connected to'the left end of a lever I26 which is pivotally supported intermediate its ends on a short shaft I21 projecting outwardly from the upright standard plate 12. The right end (as viewed in Fig. 5) of the lever I26 is pivotally secured to an internal ring gear I28 which is mounted for limited circumferential sliding movement on an annular shoulder I29 of the upright standard plate 12. By the foregoingarrangement of parts, therefore, as the link I20 moves upwardly from rotation of the handle 21, the lever I26 turns in a clockwise direction about its pivot I21, thereby forcing the-internal gear I28 to move in a clockwise direction.

The upper or outward end portions tr each of I seeding gear 64 in clockwise order.

'all the other pinions I6 are through the -other shafts 76 direction, as viewed in Fig. 4, the brackets 61 and 66 are also rocked in a clockwise direction about their respective pivot points or shafts 10, thereby causing all the gears 64 to move outwardly in a substantially radial direction away from the shaft 46 to their outward positions illustrated in Fig. 7. Thus, the operator by the single act of turning the handle 2"I the proper amount causes the gear 60 to move to the eccentric position desired and simultaneously causes the eight gears 64 also to move away to their outwardly adjusted positions, one or more of which remain'in meshing engagement with the gear 66 during this adjusting movement, as illustrated in Fig. 7.

By moving the gear 60in one radial direction to adjusted eccentric position, its effective radius is thereby increased and: in operation it is equivalent to a larger. concentric gear capable of driving at a higher rate of speed. As shown in Fig. 7, with the gears 64 and the gear 60 in eccentrically adjusted position, rotation of the shaft 46, as above described, in a clockwise direction causes the gear 60, which is now an eccentric, also to-rotate clockwise. As it so rotates in a clockwisedirection, the gear 60 engages one or more of the gears 64 and drives them in a counterclockwise direction. Upon continued clockwise movement, the gear 66 progressively breaks oil meshing engagement with 64 and successively goes into meshing engagement with the next succeeding gears 64. The gear 60 is always in driving engagement with one or more gears 64 and before driving engagement with one gear '64 is broken off the gear 60 is in definite driving engagement with the next suc- Since at least one of the gears 64 is always in driving contact with the eccentric gear 66, all of the gears 64, including those. out of meshing engagement'with the gear 60, are also caused to rotate at the same rate of speed as will be explained later. This permits the eccentric gear to pick up and become engaged with the next succeeding gear 64' without clashing since its speed of rota-' tion is synchronized with the speed of ,rotation' of the gear 60. Rotation of all the-gears is effected through the common gear Tl. For instance, if only one gear 64 is in meshing engagement with the eccentric gear 60, the driving force is transmitted from the eccentric gear 60, to the one engaged gear 64, to its one meshing gear 65 which drives one pinion 16 through the one shaft 16. Driving rotation of the one pinion 16 causes rotation of the large ear I1 with the result that caused to rotate thereby driving all. the other gears 64 back tric position so as tojincrease its effective radius,

certain of the gears the greater will be the speed of rotation of the internal gear 42 and the lower will be the speed of the dliVl n sleeve 26. Conversely, as the gear 60 moves to ivard its concentric position, the speed of rotation of the internal gear 42 iscorrespondingly lowered and the resultant speed of rotation of the driven sleeve 26 is correspondingly higher. The highest output speed of the driven sleeve 26 results when the gear 60 is in concentric position on the shaft 46 since at this time the in-- ternal gear 42 is being driven at its lowest rate of speed.

Thus, merely by rotation of the crank handle 21 which projects outside of the casing N, the operator may, even during machine operation-without stoppage or disconnection of the mechanism, adjust the speed of rotation of the driven sleeve 26 to any infinitesimal amount withinv a given range of adjustment. The adjustment is not limited to certain steps, rates or variations "of speed as is the case when separate larger or smaller gears are, injected into a gear train or when stepped cone gears and the like are employed. By sliding the gear 66 upwardly on the support-, ing block 6| any infinite amount, the speed of' the driven sleeve 26 may be correspondinglyre duced an infinite amount. The speed changing structure of the present invention is, therefore, infinitely variable with a given range or adjustment.

Also, as described, the unit is sealed, self-contained and capable of a long operable life. The

unit isan all-gear device employing gears and in manufacture and assembly. It is also comand the other gears the gears 64 are therefore caused to rotate at a higher rate of speed "than when the gear 66 was concentric. The increase of the rate of speed of the gears 64 accordingly increases the speed of rotation of all the gears in'the, gear train thereafter including the gears 65, the pinions 16,

the gear II, the gear 6!, the sleeve 43 and finally the internal gear 42. By the increase of speed of rotation 'of'the internal gear 42, asset forth in detail hereinabove, the resultant speed of ropact and may be manufactured and sold as a separate unit for application to machines and mechanisms presently in use without the necessity of modification of those machines or mechanisms in any way. In addition, in order to make the adjustment, no particular skill is required on the part of the operator since all that is required is the turning of the crank handle 21. Thus, the

cover plate need not be removed at any time for speed adjustments. Also with the gear parts operating in an oil bath the wear on the parts is reduced to a minimum.

It is also to be noted that by the foregoing allgear infinitely variable speed changing trans-' mission there is little or no loss of power when the driven sleeve 26 is put under load. When the load is applied to the driven sleeve 26, a reaction'occurs which tends to drive the internal gear 42 and the other gears in the gear train back to the driving shaft 25 so as to'drive it in the same direction as the source of power. This reaction under load, therefore, tends to drive the driving shaft 25 in the same direction in .which the source of power drives it so that power is tended to be put back into or returned to the driving shaft 25. Consequently, the loss of power through the speed control mechanism has been reduced to a minimum.

{Although one form of infinitelyvariable speed changing transmission has been described hereinbefore with reference to the accompanying drawings, it is to be understood that modifications and variations in structure may-be made without departing from the spiritand scope'of the driving shaft 25 and the driven shaft 26. For

instance, by proper modification of the parts, the internal gear could be made the driving member of the planetary train and thus connected directly with the driving shaft 26, and the sun gear could be the gear member of the planetary train whose rate of speed would be controlled by the eccentrically movable gear 60. The arrangement could also be varied in a similar respect with regard to the planet gears of the train.

What is claimed is:

1. An infinitely variable speed power transmission mechanism comprising a driving shaft, a driven shaft, a planetary gear train operably connecting the drivingshaft with the driven shaft and having three types of gears comprising a sun gear, an internal orbit gear and a plurality of planet gears in meshing engagement with said sun gear and said internal gear, one of said type of gears being the driving element of the 7 train and another of said type of gears being the driven element of the train, and means for varying the speed of movement of the third type of gear of the train to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft, means operably connecting said driving shaft and said rotatable shaft for efiecting rotation of said rotatable shaft, an eccentrically movable gear mounted on said rotatable shaft for rotative movement therewith and adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted to mesh with said movable gear in its concentric and eccentric positions and means for operably connecting said plurality of gears in driving relation to said third type of gear of the planetary train 2. An infinitely variable speed power tssion mechanismv comprising a driving shaft, a driven shaft, a planetary gear train operably connecting the driving shaft with the driven shaft and having three types of gears comprising a sun gear, an internal orbit gear and a plurality of planet gears in meshing engagement with said sun gear and said internal gear, one of said type of gears being the driving element of the'train and other of said type oftgears being the driven element of the train, and means for varying the speed of movement of the third type of gear of the train to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft,v means operably connecting said driving shaft and said rotatable shaft for eflecting rotation of said rotatable shaft, an eccentrically movable gear mounted on said rotatable shaft for rctative movement therewith and adapted to be moved relative to saidrotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted to mesh with said movable gear in its concentric and eccentric positions, said plurality of gears being adapted for outward movement away from said rotatable shaft, means for moving said movable gear to various eccentric positions, means for moving said plurality of gears outwardly away from said rotatable shaft, and means for operably connecting said plurality of gears in driving relation to said third type of gear of the planetary train.

3. An infinitely variable speed power transmission mechanism comprising a driving shaft, a driven shaft, a planetary gear train operably connecting the driving shaft with the driven shaft and having three types of gears comprising a sun gear, an internal orbit gear and a plurality of planet gears in meshing engagement with said sun gear and said internal gear, one of said type of gears being the driving element of the train and another of said type of gears being the driven element of the train, and means for varying the speed of movement of the third type of gear of the train to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft, means operably connecting said driving shaft and said rotatable shaft for effecting rotation of said rotatable shaft, an eccentrically movable gear mounted on said rotatable shaft for rotative movement therewith and adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted to mesh with said movable gear in its concentric and eccentric positions, said plurality of gears being adapted for outward movement away from said rotatable shaft, means for moving simultaneously said plurality of gears outwardly away from said rotatable shaft and said movable gear to eccentric position, and means for operably connecting said plurality of gears in driving relation to said third type of gear of the planetary train.

4. An infinitely variable speed power transmission mechanism comprising a driving shaft. a driven shaft, a planetary gear train operably connecting the driving shaft with the driven shaft and having three types of gears comprising a sun gear, an internal orbit gear and a plurality of planet gears in meshing engagement with said sun gear and said internal gear, one of said type of gears being the driving element of the train and another of said type of gears being the driven element of the train, and means for varying the speed of movement of the third type of gear of the train to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft, means operably connecting said driving shaft and said rotatable shaft for effecting rotative movement of said rotatable shaft, an eccentrically movabl'e gear mounted on said rotatable shaft for rotative movement therewith and adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted for outward movement away from said rotatable shaft, all of said plurality of gears being adapted to mesh with said movable gear when said movable gear is in concentric position and one or more of said plurality of gears being adapted when sun gear, an internal orbit gear and a plurality of planet gears in meshing engagement with said sun gear and said internal gear, one of said type of gears being the driving element of the train and another of said type of gears being the driven element of the train, and means for varying the speed of movement of the third type of gear of the train to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft, means operably connecting said driving shaft and said rotatable shaftfor efiecting rotative movement of said rotatable shaft, an eccentrically movable gear mounted on said rotatwhen inoutward position to mesh with said movable gear when said gear rotates in its eccen-, tric position, common gear means operably connected with each of said plurality of gears and adapted to be driven by those of said plurality of gears in meshing engagement with said movable gear and to drive those of said plurality of gears out of meshing engagement when said gears are in outward adjusted position, and means operably connecting said common gear means in driving relation to said third type of gear of the planetary train.

6. 'An infinitely variable speed power transmission mechanismcomprising a driving shaft, a driven shaft, a planetary gear train operably connecting the driving shaft with the driven shaft and having three types of gears comprising a sun gear, an internal orbit gear and a plurality V of planet gears in meshing engagement with said sun gear and said internal gear, one of said type of gears being the driving element of the train and another of said type of gears being the driven,

element of the train, and means for varying the speed of movement of the third type of gear of the train to effect a variation in the'speed of rotation of the driven shaft, comprising a rotatarality of gears and adapted upon rocking move-- ment to move said plurality of gears outwardly away from the point of rotation of said eccentrically movable gear and return, means for rocking said rockable members to outward-position and return upon movement of the. eccentrically movable gear to eccentric position andreturn, and means for-operably connecting said plurality of gears in driving relation to' said third type of gear of the planetary train.

7. An infinitely variable speed power transmissionmechanism comprisinga driving shaft,

is driven shaft, a planetary gear train operably,

connecting the driving shaft with the driven ing a sun gear, an internal. orbit gear-and a plurality of planet gears in meshing engagement with said sun gear and said internal gear, one of said type of gears being the .driving element of the train and another of said type of ears being the driven elementof the train, and means for varying the speed of movement of the third type of gear of the train to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft, means for rotating said shaft at a constant rate of speed, an eccentrically movable gear mounted on said rotatable shaft for rotative movement therewith and adapted .to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation. around the movable, gear and adapted to mesh with said movable gear in its concentric and eccentric positions and means for operably connecting said plurality of gears in driving relation to said third type of gear of the planetary train.

8. An infinitely .variable speed power transmission mechanisi'n comprising a driving shaft, a

driven shaft, a planetary gear train operably driving shaft, an internal orbit gear, and a plurality of planet gears in meshing engagement with said sun gear and said internal. gear and operably connected with the driven shaft, and

means for varying the speetl of movement of the internal gear of the planetary train to effect a variation in the speed of rotation'of the driven shaft, comprising a rotatable shaft, means oper ably connecting said driving shaft and said rotherewith and adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted to mesh with said movable gear in its concentric and eccentric positions, and means for operably connecting said plurality of gears in driving relation to said internal gear of the planetary train.

9. An infinitely variable speed power transmission mechanism comprising a driving shaft,

a driven shaft, a planetary gear train operably connecting the driving shaft with the driven shaft and comprising a sun gear driven by the driving shaft, an internal orbit gear, and a plurality of planet gears in meshing engagement with said sun gear and said internal gear and operably connected with the driven shaft, and means for varying the speed of movement of. the internal gear of the planetary train-to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft. means operably connecting said driven shaft and said rotatable shaft for effectin rotation of said rotatable shaft, an eccentrically movable gear mounted on-said rotatable shaft for rotative movement therewith and adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, aplurality of gears disposed in spaced relation around the movable gear and adaptedto mesh with said movable gear in its concentric and eccentric positions. said plurality of gears being adapted for outward movement away from said rotatable shaft, means for moving said movable gear to various eccentric positions; means for moving said plurality of gears outwardly away from said roshaft and having three types of gears compristatable shaft, and means for operably connecting said plurality of gears in driving relation to said internal gear of the planetary train.

10. An infinitely variable speed power transmission mechanism comprising a driving shaft, a driven shaft, a planetary gear train operably connecting the driving shaft with the driven shaft and comprising a, sun gear driven by the driving shaft, an internal orbit gear, and a plural ity of planet gears in meshing engagement with said sun gear and said internal gear and operably connected with the driven shaft, and means for varying the. speed of movement of the internal gear of the planetary train to effect a variation in the speed of rotation of the driven shaft, comprising arotatable shaft, means operably connecting said driving shaft and said rotatable shaft for effecting rotation of said rotatable shaft, an eccentrically movable gear mounted on said rotatable shaft for rotative movement therewith and adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted to I mesh with said movable gear in its concentric and eccentric positions, said plurality of gears being adapted for outward movement away from said rotatable shaft, means for moving simultaneously said plurality of gears outwardly away from said rotatable shaft and said movable gear to eccentric position, and means for operably connecting said plurality of gears in driving relation to said internal gear of the planetary train. i

11-. An infinitely variable speed power trans- I mission mechanism comprising a driving shaft,

a driven shaft, a. planetary gear train operably connecting the driving shaft with the driven shaft and comprising a sun gear driven by the driving shaft, an internal orbit gear, and a pluralityof planet gears in meshing engagement with said sun gear and said internal gear and operably connected with the driven shaft, and means for relation around the movable gear and adapted for outward movement away from said rotatable shaft, all of said plurality of gears being adapted to mesh with said movable gear when said movable gear is in concentric position and one or more of said plurality of gears being adapted when in outward position to mesh. with said movable gear when said gear rotates in an eccentric position, and means for operably connecting said plurality ,shaft for rotative movement therewith and of gears in driving relation to said internal gear a of'the planetary train.

12. An infinitely ariable speed power transmission mechanism" prising a' -driving shaft,- a driven shaft, a ma 3 gear train" operably connecting the driving "shaft with the driven shaft and comprising a sun gear driven by the driving shaft, an internal orbit gear. and a plurality of planet gears in meshing engagement with said sun gear and said internal gear and operably connected with the driven shaft,-and means for varying the speed of movement of the internal gear of th planetary train to effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft, means operably connecting said driving shaft and said rotatable shaft for effecting rotation of said rotatable shaft, an eccentrically movable gear mounted on said rotatable adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted for outward movement away from said rotatable shaft, all of said plurality of gears being adapted to mesh with said movable gear when said movable gear is in concentric position and one or more of said plurality of gears being adapted when in outward position to mesh with said movable gear when said gear rotates in an eccentric position, common gear means operably connected with each of said plurality of gears and adapted to be driven by those of said plurality of gears in meshing engagement with said movable gear and to drive those of said plurality of gears out of meshing engagement when said gears are in outward adjusted position, and means operably connecting said common gear means in driving relation to said internal gear of the planetary train.

13. An infinitely variable speed power transmission mechanism comprising'a driving shaft, a

driven shaft, a planetary gear train operably con-- necting the driving shaft with the driven shaft and comprising a sun gear driven by the driving shaft,v an internal orbit gear, and a plurality of planet gears in meshing engagement with said sun gear and said internal gear and operably connected with the driven shaft, and means for varying the speed of movement of the internal gear of the planetary trainto effect a variation in the speed of rotation of the driven shaft, comprising a rotatable shaft, means operably connecting said driving shaft and said rotatable shaft for ffecting rotation of said rotatable shaft, 'an eccentrically movable gear mounted on said rotatable shaft for rotative movement therewith and adapted to be moved relative to said rotatable shaft from concentric to eccentric position and return, a plurality of gears disposed in spaced relation around the eccentrically movable gear and adapted to mesh with said movable gear as it rotates in its concentric and eccentric positions, rockable means for supporting said plurality of gears and adapted upon rocking movement to move said plurality of gears outwardly away from the point of rotation of said eccentrically movable gear and return, means for rocking said rockable members and a driven member comprising an eccentrically movable gear operably connected with said driving member for rotative movement and adapted to be moved from concentric position to eccentric position and return, a plurality of gears disposed in spaced relation around the eccentrically movable scar and adapted to mesh with said movable ear as it rotates irrits concentric and eccentric positions, and means for operably connecting said plurality of gears in driving relationto the driven f member.

15, An infinitely variable speed transmission adapted to operably connect a driving member and a driven member comprising an eccen'trically movable gear operably connected with said driving member for rotative movement and adapted .to be moved from concentric position to eccentric position and return, aplurality of gears disposed in spaced relation around the eccentrically movable gearand adapted to mesh with said movable gear as it rotates in its concentric and eccentric aa'zaaao positions, said plurality of gears being adapted for outward movement away from the point of rotation of said movable gear, means for moving said movable gear to various eccentric positions, means for moving said plurality of gears outwardly away from said center of rotation of said movable gear, and means for operably connecting said plurality of gears in driving relation to the driven member.

16. An infinitely variable speed transmission concentric position and one or more of said plurality of gears being adapted when in outward position to mesh with said movable gear when said movable gear rotates in its eccentric position, and means for operably connecting said plurality of gears in driving relation to the'driven member. 7

1'7. An infinitely variable speed transmission adapted to'operably connect a driving member and a driven member comprising an eccentrically movable gear operably connected with said driving member for rotative movement and adapted to be moved from concentric position to eccentric position and return, a plurality of gears disposed in spaced relation around the movable gear and adapted for outward movement away from the point ,of rotation of said movable gear, all of said movement to move said plurality of gears outwardly away from the point of rotation of said eccentrically movable gear and return, means tor rocking said rockable members to outward position and return upon movement of the eccentrieally movable gear to eccentric position and return, and means for operably connecting said plurality of gears in driving relation to. the driven member.

19. A variable speed power transmitting mechanism comprising a driving member, a driven member, a planetary gear train operatively connecting said driving member with the driven member comprising a sun gear, a plurality of planet gears in meshing engagement with said sun gear and an internal orbit gear in. meshing engagement with said planet gears, and means for varying the'speed of rotation of said internal gear to effect a variation in the speed of rotation gear operably connectedwith and driven by said driving member and adapted to be moved relative to its point of rotation from concentric to eccentric position and return, -and means operably connecting said eccentrically movable gear in its concentric and eccentric positions with said internal ear.

20. A variable speed power transmitting mechanism comprising a driving member, a driven member, a planetary gear train operatively con- 1 necting said driving member with the driven member comprising a sun gear adapted to be driven by the driving member, a plurality df planet gears in meshing engagement with said a sun gear and operably engaged with the driven 0 gears, and means for varying the speed of rotation plurality of gears being adapted to mesh with said movable gear when said movable gear is in concentric position and one or more of said plurality of gears being adapted when in outward position to mesh with said movable gear when said movable gear rotates in its eccentric position, common gear means operably connected with each of said plurality of gears and adapted to be driven by those of said plurality of gears in meshing engagement with said movable gear and to drive those of said plurality of gears out of meshing engagement when said plurality of gears are in outward adjusted position, andmeans operably connecting said common gear means in driving relation to said driven member.

18. An infinitely variable speed transmission adapted to operably connect a driving member and a driven member comprising an eccentrically movable gearoperably connected with said driving member for rotative movement and adapted to be moved from'concentric position to eccentric position and return, a plurality of gears disposed in spaced relation around the eccentrically movable gear and adapted to mesh with said movable gear as it rotates in its concentric and eccentric positions, rockable means for supporting said plurality of gears and adapted upon rocking of said internal gear to efieot a variation in the speed of rotation oi the driven member comprising an eccentric gear operably connected with and driven by said driving member and adapted to be moved relative to its point of rotation from concentric to eccentric position and return, and means operably connecting said eccentrically movable gear in its concentric and eccentric positions with said internal gear.

21. A variable speed power transmission mechanism comprising a driving member, a driven member, a planetary gear train operably connecting the driving member with the driven member and having three types of gears comprising a sun gear, an internal orbit gearand a plurality of planet gears in meshing engagement with said sun gear and said internal gear, one or said types of gears being the driving element of the train, and another or said type oi gears being the driven element or the train, and means for varyingthe speed of movement of the third type of gear or the planetary train to effect a variation in the speed of rotation of the driven membercomprising an eccentric gear operably connected with and driven by said driving member and adapted to be moved relative to its point of rotation from or the driven member comprising an eccentric CERTIFICATE OF CORRECTION.- Pa-t'ent Nos ZJ769J+Z9Q May 22, 19145.

- GEOFFREY n, HARRY.

It is hereby certified that error appears in the printed specificet'ion of the above numbered wtent requiring correction as follows: Page '6, first column, line 56, claim 2, for "ether" read --another-; p ge 7, second 001- mun line 62, claim 9, for "driven" read "drivingpage 8, first column,

line 146, claim 11, for "rotatble" read. -rota'tab1e-; and the said Letters Petentlshould be read With this correction therein that the same may con form to the record of the case in the Patent Officea I Signed. and sealed this 21st day of Angust, A; D. 1915.

Leslie Frazer (Sel) First Assistant Commissioner of Patents. 

